CN112377381A - Electric proportional plunger pump and variable control device thereof - Google Patents
Electric proportional plunger pump and variable control device thereof Download PDFInfo
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- CN112377381A CN112377381A CN202011337842.8A CN202011337842A CN112377381A CN 112377381 A CN112377381 A CN 112377381A CN 202011337842 A CN202011337842 A CN 202011337842A CN 112377381 A CN112377381 A CN 112377381A
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- 230000006835 compression Effects 0.000 claims abstract description 37
- 238000007906 compression Methods 0.000 claims abstract description 37
- 230000036316 preload Effects 0.000 claims description 6
- 230000000694 effects Effects 0.000 abstract description 9
- 239000003921 oil Substances 0.000 description 66
- 238000006073 displacement reaction Methods 0.000 description 7
- 230000005611 electricity Effects 0.000 description 6
- 238000007789 sealing Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 230000001737 promoting effect Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000001960 triggered effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005065 mining Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 239000002904 solvent Substances 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/28—Control of machines or pumps with stationary cylinders
- F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B1/295—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/26—Control
- F04B1/30—Control of machines or pumps with rotary cylinder blocks
- F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
- F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
Abstract
The invention discloses a variable control device of an electric proportional plunger pump, which comprises: a high pressure port; a control port; the electro-proportional valve is positioned at the first control position and used for communicating the high-pressure port to two ends of the electro-proportional valve core, and the electro-proportional valve is positioned at the second control position and used for communicating the control port to two ends of the electro-proportional valve core of the electro-proportional valve; a variable compression elastic device is arranged between the variable piston and the electro-proportional valve core, and a cavity between the variable piston and the electro-proportional valve core is connected with a one-way valve structure of which the control port is communicated to the cavity in a one-way; and the pressure control valve conducts the high-pressure port and the control port when the high-pressure port exceeds a set value, and conducts the control port to the oil return port when the high-pressure port is lower than the set value. The problem that the control effect of the variable pump is not good can be effectively solved. The invention also discloses the electric proportional plunger pump comprising the variable control device of the electric proportional plunger pump.
Description
Technical Field
The invention relates to the technical field of variable pumps, in particular to a variable control device of an electric proportional plunger pump, and further relates to the electric proportional plunger pump comprising the variable control device of the electric proportional plunger pump.
Background
The plunger pump has the advantages of high rotating speed, high pressure, compact structure, easy variable control and the like, and is widely adopted by various hydraulic transmission systems. With the development of engineering machinery, mining machinery, automobile manufacturing and other technologies, the requirements of proportional control, servo control, stepless speed regulation and the like are also provided for hydraulic elements of a hydraulic system. The variable of the axial plunger pump is mainly to adjust the swing angle of the swash plate by the variable piston pushing the inner swash plate to swing. However, the control effect of the inclination angle of the existing swash plate is not good, the pushing angle is difficult to control accurately, and the emergency unloading is difficult to carry out well.
In summary, how to effectively solve the problem of poor control effect of the variable displacement pump is a problem that needs to be solved urgently by those skilled in the art at present.
Disclosure of Invention
In view of the above, a first object of the present invention is to provide an electro-proportional plunger pump variable control device, which can effectively solve the problem of poor control effect of the variable pump, and a second object of the present invention is to provide an electro-proportional plunger pump including the above-mentioned electro-proportional plunger pump variable control device.
In order to achieve the first object, the invention provides the following technical scheme:
an electro-proportional plunger pump variable control device comprising:
a high pressure port;
a control port;
the electro-proportional valve is positioned at a first control position and used for communicating the high-pressure port to two ends of an electro-proportional valve core of the electro-proportional valve, and the electro-proportional valve is positioned at a second control position and used for communicating the control port to two ends of the electro-proportional valve core of the electro-proportional valve, and after the electromagnetic valve is electrified, electromagnetic thrust is generated to push the electro-proportional valve core to be positioned at the second control position, and the two ends of the electro-proportional valve core are conducted as the current increases and the thrust on the electro-proportional valve core increases;
a variable compression elastic device which is opposite to the pushing direction of the electro-proportional valve core and the electromagnetic pushing direction is arranged between the variable piston and the electro-proportional valve core, and a cavity between the variable piston and the electro-proportional valve core is connected with a one-way valve structure of which the control port is communicated to the cavity in a one-way manner;
and the pressure control valve conducts the high-pressure port and the control port when the pressure of the high-pressure port exceeds a set value, and conducts the control port to the oil return port when the pressure of the high-pressure port is lower than the set value.
According to the technical scheme, when the variable control device of the electric proportional plunger pump is applied, the high-pressure port is communicated to the oil outlet of the electric proportional variable pump, and the variable piston is abutted against the swash plate of the electric proportional variable pump to transmit the driving force. When the oil pressure of high-pressure port is not higher than the setting value all the time, say that present oil pressure belongs to normal oil pressure promptly, the control port passes through pressure control valve intercommunication oil return opening, mainly has following two kinds of operating condition this moment: in the first working state, when the electro-proportional valve is not electrified or the current is very small, the electro-proportional valve is located at a first control position, the high-pressure port is communicated to two ends of a valve core of the electro-proportional valve, high-pressure oil enters between the variable piston and the electro-proportional valve core, and because the oil pressure is very high, the variable piston is pushed to move so as to push the swash plate to rotate so as to overcome a return spring of the electro-proportional variable pump, so that the swing angle of the swash plate is zero, and the electro-proportional variable pump does not output flow; and in the second working state, when the current of the electro-proportional valve is larger, the electro-proportional valve core is pushed to move at the moment so as to enter a second control position, the cavity between the variable piston and the electro-proportional valve core is communicated with the oil return port through the control port, and oil bodies at the end part of the variable piston enter the oil return port so as not to generate thrust on the variable piston any more, and the electro-proportional valve core gradually increases the thrust on the variable compression elastic device along with the increase of the current at the moment, and the pressure at two ends of the variable compression elastic device is increased and compressed so as to enable the variable piston to move towards the direction close to the electro-proportional valve core, so that the inclination angle of the swash plate is gradually increased, so that the oil output of the variable pump is increased until the maximum swing angle is reached, namely, the maximum oil output is kept, and. When the pressure of the high-pressure port is very high, the pressure of an oil outlet of the variable pump is very high, when the pressure exceeds a set value, the pressure control valve is triggered, the control port is communicated with the high-pressure port through the pressure control valve, the one-way valve structure is jacked open by the control port at the moment, high-pressure oil enters a cavity between the variable piston and the electro-proportional valve core through the one-way valve structure, and no matter the electro-proportional valve is located at the first control position or the second control position at the moment, the cavity between the variable piston and the electro-proportional valve core can be guaranteed to be in a high-pressure state because the control port is not communicated with an oil return port any more, the high-pressure oil can push the variable piston to move towards the direction far away from the electro-proportional valve core, so that the swing angle of the swash plate is reduced to zero, and. Among this electricity proportion plunger pump variable control device, set up through electricity proportional valve and pressure control valve to when making high-pressure port oil pressure normal, can adjust variable piston position through electricity proportional valve, and then adjust variable piston inclination, and when high-pressure port oil pressure surpassed standard, through pressure regulating valve, through the check valve, in order to lead high-pressure oil fast to variable piston department, in order to promote variable piston to remove to promoting the sloping cam plate and rotate, with closed variable pump. In conclusion, the variable control device of the electric proportional plunger pump can effectively solve the problem that the control effect of the variable pump is not good.
Preferably, the control device further comprises a preloaded elastic device with the thrust force consistent with the electromagnetic thrust direction, so as to push the electric proportional valve core to move towards the second control position of the electric proportional valve.
Preferably, the electro-proportional valve further comprises an electro-proportional valve body, the electro-proportional valve spool is inserted into the electro-proportional valve body, and a variable elastic device opposite to the electromagnetic thrust direction is further arranged between the electro-proportional valve body and the electro-proportional valve spool.
Preferably, an axial passage communicated with the control port is arranged in the middle of the electro-proportional valve core, a valve seat is arranged between the variable compression elastic device and the electro-proportional valve core, an opening is formed at the valve seat by the axial passage, the opening of the axial passage is closed when the valve seat and the electro-proportional valve core are abutted against each other, and the valve seat, the axial passage and the variable compression elastic device form the one-way valve structure.
Preferably, the electro-proportional valve is a two-position three-way electro-proportional valve.
Preferably, the preload elastic device is arranged at one end of the electro proportional valve core far away from the variable piston and is a compression spring sleeved on the electromagnet.
Preferably, the lifting elastic device is a compression spring, and is sleeved on the electric proportional valve core, one end of the compression spring abuts against a shoulder at the end of the electric proportional valve core, and the other end of the compression spring abuts against the electric proportional valve body.
Preferably, one side of the variable piston, which is close to the electro-proportional valve core, is provided with an open groove, and one end of the variable compression elastic device is installed in the open groove and can be compressed until the variable piston abuts against the end face of the electro-proportional valve body.
Preferably, a load sensitive control valve is further included such that the high pressure port can communicate with the control port through the load sensitive valve.
In order to achieve the second object, the invention further provides an electro-proportional plunger pump, which comprises any one of the variable control devices of the electro-proportional plunger pump, and further comprises a swash plate, wherein variable pistons of the variable control devices of the electro-proportional plunger pump and the swash plate transmit thrust to push the swash plate to swing. Since the variable control device of the electric proportional plunger pump has the technical effects, the electric proportional plunger pump with the variable control device of the electric proportional plunger pump also has the corresponding technical effects.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic cross-sectional structural diagram of an electro-proportional plunger pump variable control device according to an embodiment of the present invention;
fig. 2 is a schematic oil circuit diagram of the variable control device of the electro-proportional plunger pump according to the embodiment of the invention.
The drawings are numbered as follows:
the variable displacement hydraulic control valve comprises a variable piston 1, a variable compression elastic device 2, a valve seat 3, an electro-proportional valve core 4, a high-pressure port 5, a variable elastic device 6, a control port 7, an electromagnet 8, an electro-proportional valve body 9, a pressure control valve 10, a load sensitive valve 11 and a preload elastic device 12.
Detailed Description
The embodiment of the invention discloses a variable control device of an electric proportional plunger pump, which is used for effectively solving the problem of poor control effect of the variable pump.
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1-2, fig. 1 is a schematic cross-sectional structural diagram of an electrical proportional plunger pump variable control device according to an embodiment of the present invention; fig. 2 is a schematic oil circuit diagram of the variable control device of the electro-proportional plunger pump according to the embodiment of the invention.
In one embodiment, the present implementation provides an electro-proportional piston pump variable control device to control a swash plate inclination angle of a variable pump via the variable control device to adjust a variable pump output. Specifically, the variable control device includes a high-pressure port 5, a control port 7, an electro proportional valve, a pressure control valve 10, and a variable piston 1. Typically in use, the high pressure port 5 is adapted to communicate with a working outlet of the variable displacement pump for direct access to high pressure oil at the working outlet, and the control port 7, in use, communicates with an oil return port via a pressure control valve 10.
And the electric proportional valve is used for communicating the high-pressure port 5 to two ends of the electric proportional valve core 4 when positioned at a first control position. That is, when the electro proportional valve element 4 of the electro proportional valve moves to the first control position, the high-pressure oil at the high-pressure port 5 is caused to enter both sides of the electro proportional valve element by the electro proportional valve element 4. And when the second control position is positioned, the control port 7 is communicated to two ends of the electro-proportional valve core 4 of the electro-proportional valve, so that the oil pressure at two ends of the electro-proportional valve core 4 is equal to that of the control port 7 at the moment. Specifically, the electro-proportional valve can be a two-position three-way electro-proportional valve, two ports on one side are respectively communicated with the high-pressure port 5 and the control port 7, and one port on the other side is respectively communicated with the cavities at two ends of the electro-proportional valve core 4.
The electromagnetic proportional valve electromagnetic valve generates electromagnetic thrust after being electrified, generally, the electromagnet 8 is arranged inside, and the internal connection current can generate outwards-driven thrust, namely the electromagnetic thrust, on the internal electromagnet 8. The electromagnetic thrust acts to push the electro-proportional valve element 4 to be in the second control position and increases as the current increases. Under a general control condition, two ends of the electro proportional valve core 4 are conducted, so that hydraulic oil entering the two ends of the electro proportional valve core 4 cannot generate thrust for pushing the electro proportional valve core 4 to move.
And a variable compression elastic device 2 with the pushing direction of the electro-proportional valve core 4 opposite to the electromagnetic pushing direction is arranged between the variable piston 1 and the electro-proportional valve core 4, so that the electromagnetic pushing force is resisted by the variable compression elastic device 2. The variable compression elastic device 2 is arranged between the variable piston 1 and the electro-proportional valve core 4, so that two ends respectively form acting forces on the variable piston 1 and the electro-proportional valve core 4, and the acting forces are opposite. The cavity between the variable piston 1 and the electro-proportional valve element 4 is connected with the control port 7 through a one-way valve structure which is communicated to the cavity in a one-way mode, so that when the oil pressure of the control port 7 is higher than that of the cavity, the one-way valve structure is communicated, high-pressure oil can flow to the cavity from the control port 7, and acts on the end portion of the variable piston 1 and two ends of the electro-proportional valve element.
The pressure control valve 10 conducts the high pressure port 5 and the control port 7 when the high pressure port 5 exceeds a set value, and conducts the control port 7 to an oil return port when the high pressure port 5 is lower than the set value, so that oil bodies in the control port 7 return to the oil tank. So that when the pressure is high, the pressure control valve 10 automatically conducts the high pressure port 5 and the control port 7, so that the high pressure oil can be quickly guided to the cavity between the variable piston 1 and the electro proportional valve core 4 through the above-mentioned check valve to act on the variable piston 1. When the oil pressure of the high-pressure port 5 is low, the control port 7 is communicated with the oil return port, and the work of the variable piston 1 cannot be interfered.
According to the technical scheme, when the variable control device of the electric proportional plunger pump is applied, the high-pressure port 5 is communicated to an oil outlet of the electric proportional variable pump, and the variable piston 1 is abutted against a swash plate of the electric proportional variable pump to transmit driving force. When the oil pressure of the high-pressure port 5 is not higher than the set value all the time, that is, the current oil pressure belongs to the normal oil pressure, the control port 7 is communicated with the oil return port through the pressure control valve 10, and at the moment, the following two working states are mainly available: in the first working state, when the electro-proportional valve is not electrified or the current is very small, the electro-proportional valve is located at a first control position, the high-pressure port 5 is communicated to two ends of a valve core of the electro-proportional valve, and high-pressure oil enters between the variable piston 1 and the electro-proportional valve core 4, and because the oil pressure is very high, the variable piston 1 is pushed to move so as to push the swash plate to rotate so as to overcome a return spring of the electro-proportional variable pump, so that the swing angle of the swash plate is zero, and the electro-proportional variable pump does not output flow; and in a second working state, when the current of the electro-proportional valve is larger, the electro-proportional valve core 4 is pushed to move to enter a second control position, the cavity between the variable piston 1 and the electro-proportional valve core 4 is communicated with an oil return port through the control port 7, oil bodies at the end part of the variable piston 1 enter the oil return port to prevent thrust from being generated on the variable piston 1, and the electro-proportional valve core 4 gradually increases the thrust on the variable compression elastic device 2 along with the increase of the current at the moment, and the pressure at two ends of the variable compression elastic device 2 is increased and is compressed to enable the variable piston 1 to move towards the direction close to the electro-proportional valve core 4 so as to gradually increase the inclination angle of the swash plate, so that the oil output of the variable pump is increased until the variable pump is at the maximum swing angle, namely, the maximum oil output is kept, and flow regulation is further realized. When the pressure of the high-pressure port 5 is very high, the pressure of an oil outlet of the variable pump is very high, when the pressure exceeds a set value, the pressure control valve 10 is triggered, the control port 7 is communicated with the high-pressure port 5 through the pressure control valve 10, at the moment, the high pressure can push the one-way valve structure open, so that high-pressure oil enters a cavity between the variable piston 1 and the electro-proportional valve core 4 through the one-way valve structure, at the moment, no matter the electro-proportional valve is located at the first control position or the second control position, the control port 7 is not communicated with an oil return port any more, so that the cavity between the variable piston 1 and the electro-proportional valve core 4 can be ensured to be in a high-pressure state, and the high-pressure oil can push the variable piston 1 to move in a direction away from the electro-proportional valve core 4, so as to push the swash plate swing angle to be reduced to. In this electricity proportion plunger pump variable control device, set up through electricity proportional valve and pressure control valve 10 to when making 5 oil pressures of high-pressure port normal, can adjust variable piston 1 position through electricity proportional valve, and then adjust variable piston 1 inclination, and when 5 oil pressures of high-pressure port surpass standard, through pressure regulating valve, through the check valve, in order to lead high-pressure oil to variable piston 1 department fast, rotate to promoting the swash plate in order to promote variable piston 1 to remove, with closed variable pump. In conclusion, the variable control device of the electric proportional plunger pump can effectively solve the problem that the control effect of the variable pump is not good.
As described above, when the electro-proportional valve is suddenly de-energized during normal operation, the electromagnetic thrust force disappears immediately at this time, and when the electromagnet 8 is in a failure state, the electro-proportional valve immediately enters the first control position, the variable displacement pump immediately drops to zero displacement, the host system stops operating instantly, and a great potential safety hazard exists for the engineering mechanical device. Based on this, it is also preferable to further include a preloaded elastic device 12 whose thrust is in accordance with the direction of the electromagnetic thrust to urge the electro-proportional valve spool 4 to move toward the second control position of the electro-proportional valve. So that when the electro-proportional valve is de-energized, the electro-proportional valve spool 4 is still maintained at a certain height by preloading the elastic means 12, so that the swash plate of the variable displacement pump is maintained at a small inclination angle, thereby ensuring a small flow output. For convenience of arrangement, the preload elastic device 12 may be disposed at an end of the electro proportional valve element 4 away from the variable piston 1, specifically, a compression spring may be used, and specifically, the preload elastic device may be integrated with the electromagnet 8.
Further, in order to better control the movement of the electro-proportional valve element 4, it is preferable that the variable elastic device 6 is further included, specifically, if the electro-proportional valve element 4 is inserted into the electro-proportional valve body 9, wherein the variable elastic device 6 is further disposed between the electro-proportional valve body 9 and the electro-proportional valve element 4 in a direction opposite to the electromagnetic thrust direction. Specifically, the variable elastic device 6 may be installed at an end of the electro-proportional valve spool 4 remote from the variable piston 1. As at this end, the electro proportional valve element 4 is provided with a shoulder, wherein the lifting elastic means 6 is a compression spring, which is fitted over the electro proportional valve element 4, with one end abutting against the shoulder and the other end abutting against the electro proportional valve body 9.
Further, in order to facilitate the above-mentioned check valve structure, the whole of the valve core of the electro-proportional valve is more compact, and it is preferable that an axial passage communicating with the control port 7 is provided in the middle of the valve core 4, wherein a valve seat 3 is provided between the variable compression elastic device 2 and the valve core 4, and the axial passage forms an opening at the valve seat 3, and the valve seat 3 closes the opening of the axial passage when abutting against the valve core 4, so that the valve seat 3, the axial passage and the variable compression elastic device 2 form the above-mentioned check valve structure, when the control port 7 is communicated with the high pressure port 5 or other reasons, so that the axial passage is in a high oil pressure state, at this time, the high oil pressure acts on the valve seat 3, and overcomes the acting force of the variable compression elastic device 2 acting on the valve seat 3, and pushes the valve seat 3 away from the opening, so as to form a certain opening degree, so that the high oil flows into the space between the valve seat 3 and the variable piston 1 from the space between the And (3) removing the solvent. When the oil pressure in the axial channel is smaller, the valve seat 3 is tightly attached to the valve core of the electric proportional valve under the action of the variable compression elastic device 2, the opening is closed, and the one-way valve structure is closed. In order to make the valve seat 3 and the electro-proportional valve element 4 better fit, it is preferable that a spherical concave surface is formed on one side of the valve seat 3 facing the electro-proportional valve element 4, and a spherical convex surface is formed on an end portion of the electro-proportional valve element 4 to fit with the spherical concave surface of the valve seat 3. Wherein a column part is arranged on the valve seat 3 so that the variable compression elastic device 2 is sleeved on the valve seat 3.
Specifically, in order to facilitate the setting of the electro-proportional valve, it is preferable that the electro-proportional valve body 4 is columnar, the electro-proportional valve body 9 is provided with a high pressure port 5, an intermediate port and a control port 7 which are sequentially arranged in parallel in the extending direction of the electro-proportional valve body 4, wherein the intermediate port is guided to both ends of the electro-proportional valve body 4 through a passage, wherein the extending direction of the electro-proportional valve body 4 is provided with two first annular grooves corresponding to the high pressure port 5 and two second annular grooves corresponding to the control port 7 which are arranged in parallel, so that when the electro-proportional valve body 4 moves to a first control position, the first annular grooves can be correspondingly communicated with the intermediate port, and when the second control position is moved, the second annular grooves can be correspondingly communicated with the intermediate port. Wherein the groove bottom of the second annular groove is communicated with the axial channel through the radial channel. After the preload elastic device 12 is arranged, a little gap exists between the second annular groove and the middle opening, so that the electro-proportional valve core 4 has a certain opening degree, and the variable displacement pump has a small flow output to ensure the operation of the system. In order to conveniently insert the electro-proportional valve body 9, a plurality of annular sealing grooves are formed in the outer side of the electro-proportional valve body 9, annular sealing rings are arranged in the annular sealing grooves, particularly, the two sides of the middle opening, the two sides of the control opening 7 and the two sides of the high-pressure opening 5 are provided with the annular sealing rings, and the end portions of the insertion section of the electro-proportional valve body 9 are correspondingly provided with the sealing rings.
Furthermore, an open slot is formed in one side, close to the electro-proportional valve core 4, of the variable piston 1, the variable compression elastic device 2 is installed into the open slot, one end of the variable compression elastic device abuts against the bottom of the open slot, the other end of the variable compression elastic device is sleeved on the valve seat 3, the variable compression elastic device can compress the variable piston 1 to abut against the end face of the electro-proportional valve body 9, so that the swash plate of the variable pump keeps the maximum swing angle, and the valve seat 3 is located in the open slot at the moment.
The swash plate is characterized by further comprising a load sensitive control valve, so that when the main engine is in a standby state and does not need to work during working, the high-pressure port 5 can be communicated with the control port 7 through the load sensitive valve 11, pressure oil of the high-pressure port 5 enters a cavity between the variable piston 1 and the electro-proportional valve core 4 through a one-way valve structure, and the swash plate is in a small swing angle state. The optimized load sensitive control valve comprises a two-position three-way hydraulic control reversing valve, two oil ports on one side are respectively connected with a high-pressure port 5 and an oil return port, one oil port on the other side is communicated with a pressure control valve 10, namely the two-position three-way hydraulic control reversing valve is connected between the pressure control valve 10 and the oil return port, when a valve core moves to a first position side, the oil return port is communicated with the pressure control valve 10, when the valve core moves to a second position side, the high-pressure port 5 is communicated with the pressure control valve 10, a first position side valve core control port 7 is communicated with the high-pressure port 5, a second position side valve core control port 7 is communicated with one side of an adjustable throttling valve on an oil way main road, which is far away from a variable pump, and is provided with an adjustable compression spring, wherein one side of the adjustable throttling valve, which is close to the variable pump, is one side communicated with the variable pump, so that, that is, a small amplitude is sufficiently large, the spool moves to the second position side, otherwise the spool moves to the first position side. Correspondingly, the pressure control valve 10 may also be a two-position three-way directional valve, the compression spring on one side is used to push the valve core to move to the load-sensitive valve 11 to communicate with the control port 7, and the high-pressure oil passing through the high-pressure port 5 reaches enough oil pressure to push the valve core to overcome the acting force of the compression spring to move to make the high-pressure port 5 communicate with the control port 7.
Based on the variable control device of the electro-proportional plunger pump provided in the above embodiment, the invention also provides the electro-proportional plunger pump, the electro-proportional plunger pump comprises any one of the variable control devices of the above embodiments, and further comprises a swash plate, and a variable piston of the variable control device of the electro-proportional plunger pump and the swash plate transmit thrust to push the swash plate to swing. Since the variable control device of the electric proportional plunger pump in the above embodiment is adopted in the electric proportional plunger pump, please refer to the above embodiment for the beneficial effect of the electric proportional plunger pump.
The embodiments in the present description are described in a progressive manner, each embodiment focuses on differences from other embodiments, and the same and similar parts among the embodiments are referred to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. An electro-proportional plunger pump variable control device, comprising:
a high pressure port;
a control port;
the electro-proportional valve is positioned at a first control position and used for communicating the high-pressure port to two ends of an electro-proportional valve core of the electro-proportional valve, and the electro-proportional valve is positioned at a second control position and used for communicating the control port to two ends of the electro-proportional valve core, after the electromagnetic valve is electrified, electromagnetic thrust is generated to push the electro-proportional valve core to be positioned at the second control position, the thrust on the electro-proportional valve core is increased along with the increase of current, and two ends of the electro-proportional valve core are conducted;
a variable compression elastic device which is opposite to the pushing direction of the electro-proportional valve core and the electromagnetic pushing direction is arranged between the variable piston and the electro-proportional valve core, and a cavity between the variable piston and the electro-proportional valve core is connected with a one-way valve structure of which the control port is communicated to the cavity in a one-way manner;
and the pressure control valve conducts the high-pressure port and the control port when the pressure of the high-pressure port exceeds a set value, and conducts the control port to the oil return port when the pressure of the high-pressure port is lower than the set value.
2. The electro-proportional plunger pump variable control device of claim 1, further comprising a preloaded elastic device having a thrust force aligned with the electromagnetic thrust force to urge the electro-proportional valve spool toward the second control position of the electro-proportional valve.
3. The electro-proportional plunger pump variable control device of claim 2, wherein the electro-proportional valve further comprises an electro-proportional valve body into which the electro-proportional valve spool is inserted, and a lifting elastic device opposite to the electromagnetic thrust direction is further provided between the electro-proportional valve body and the electro-proportional valve spool.
4. The variable control device of the electro-proportional plunger pump according to claim 3, wherein an axial passage communicating with the control port is provided in the middle of the electro-proportional valve core, a valve seat is provided between the variable compression elastic device and the electro-proportional valve core, the axial passage forms an opening at the valve seat, the valve seat closes the axial passage opening when abutting against the electro-proportional valve core, and the valve seat, the axial passage and the variable compression elastic device constitute the one-way valve structure.
5. The electro-proportional plunger pump variable control device of claim 4, wherein the electro-proportional valve is a two-position three-way electro-proportional valve.
6. The electro-proportional plunger pump variable control device of claim 5, wherein the pre-load elastic device is arranged at one end of the electro-proportional valve core far away from the variable piston and is a compression spring sleeved on an electromagnet.
7. The variable control device of the electro-proportional plunger pump according to claim 6, wherein the variable elastic device is a compression spring, which is sleeved on the electro-proportional valve core, and one end of the variable elastic device abuts against the shoulder at the end of the electro-proportional valve core, and the other end of the variable elastic device abuts against the electro-proportional valve body.
8. The electro-proportional plunger pump variable control device of claim 7, wherein a side of the variable piston near the electro-proportional valve core is provided with an open slot, and one end of the variable compression elastic device is installed in the open slot and can be compressed until the variable piston is pressed against the end face of the electro-proportional valve body.
9. The electro-proportional plunger pump variable control device of any of claims 1-8, further comprising a load sensitive control valve such that the high pressure port can communicate with the control port through the load sensitive valve.
10. An electro-proportional piston pump comprising a swash plate, and further comprising an electro-proportional piston pump variable control device according to any one of claims 1 to 9, a variable piston of the electro-proportional piston pump variable control device transmitting a thrust force with the swash plate to push the swash plate to swing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011337842.8A CN112377381A (en) | 2020-11-25 | 2020-11-25 | Electric proportional plunger pump and variable control device thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011337842.8A CN112377381A (en) | 2020-11-25 | 2020-11-25 | Electric proportional plunger pump and variable control device thereof |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112377381A true CN112377381A (en) | 2021-02-19 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011337842.8A Pending CN112377381A (en) | 2020-11-25 | 2020-11-25 | Electric proportional plunger pump and variable control device thereof |
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| Country | Link |
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| CN (1) | CN112377381A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113446280A (en) * | 2021-06-30 | 2021-09-28 | 北京航空航天大学宁波创新研究院 | Bidirectional differential pressure controller and hydraulic equipment |
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| DE102013224113A1 (en) * | 2013-11-26 | 2015-05-28 | Robert Bosch Gmbh | hydraulic motor |
| CN105134578A (en) * | 2015-07-30 | 2015-12-09 | 徐州重型机械有限公司 | Plunger pump with energy recycling function |
| CN110985459A (en) * | 2019-12-12 | 2020-04-10 | 圣邦集团有限公司 | Hydraulic control system of load-sensitive pump |
| US20200263675A1 (en) * | 2015-12-25 | 2020-08-20 | Kawasaki Jukogyo Kabushiki Kaisha | Displacement adjusting device of swash plate pump |
| CN214424647U (en) * | 2020-11-25 | 2021-10-19 | 力源液压（苏州）有限公司 | Electric proportional plunger pump and variable control device thereof |
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2020
- 2020-11-25 CN CN202011337842.8A patent/CN112377381A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
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| DE102013224113A1 (en) * | 2013-11-26 | 2015-05-28 | Robert Bosch Gmbh | hydraulic motor |
| CN105134578A (en) * | 2015-07-30 | 2015-12-09 | 徐州重型机械有限公司 | Plunger pump with energy recycling function |
| US20200263675A1 (en) * | 2015-12-25 | 2020-08-20 | Kawasaki Jukogyo Kabushiki Kaisha | Displacement adjusting device of swash plate pump |
| CN110985459A (en) * | 2019-12-12 | 2020-04-10 | 圣邦集团有限公司 | Hydraulic control system of load-sensitive pump |
| CN214424647U (en) * | 2020-11-25 | 2021-10-19 | 力源液压（苏州）有限公司 | Electric proportional plunger pump and variable control device thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113446280A (en) * | 2021-06-30 | 2021-09-28 | 北京航空航天大学宁波创新研究院 | Bidirectional differential pressure controller and hydraulic equipment |
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